Cooling hole with curved metering section

ABSTRACT

A gas turbine engine component having a cooling hole includes a first wall having a cooling hole inlet, a second wall generally opposite the first wall and having a cooling hole outlet, a metering section extending downstream from the inlet and having a hydraulic diameter (d h ), and a diffusing section extending from the metering section to the outlet. The metering section includes a substantially convex first surface extending from a first end to a second end, a substantially concave second surface extending from a third end to a fourth end, and first and second curved portions connecting the ends of the first and second surfaces.

CROSS-REFERENCE TO RELATED APPLICATION

This application is a continuation-in-part of U.S. application Ser. No.14/478,630, filed Sep. 5, 2014, and entitled “COOLING HOLE WITH CURVEDMETERING SECTION”, which is a continuation of U.S. application Ser. No.13/544,125, filed Jul. 9, 2012, and entitled “COOLING HOLE WITH CURVEDMETERING SECTION”, which claims priority to U.S. Provisional ApplicationNo. 61/599,378, filed on Feb. 15, 2012 and entitled “COOLING HOLE WITHCURVED METERING SECTION” and U.S. Provisional Application No.61/599,381, filed on Feb. 15, 2012 and entitled “TRI-LOBED COOLING HOLEAND METHOD OF MANUFACTURE”, the disclosures of which are incorporated byreference in their entirety.

BACKGROUND

This invention relates generally to turbomachinery, and specifically toturbine flow path components for gas turbine engines. In particular, theinvention relates to cooling techniques for airfoils and other gasturbine engine components exposed to hot working fluid flow, including,but not limited to, rotor blades and stator vane airfoils, endwallsurfaces including platforms, shrouds and compressor and turbinecasings, combustor liners, turbine exhaust assemblies, thrust augmentorsand exhaust nozzles.

Gas turbine engines are rotary-type combustion turbine engines builtaround a power core made up of a compressor, combustor and turbine,arranged in flow series with an upstream inlet and downstream exhaust.The compressor section compresses air from the inlet, which is mixedwith fuel in the combustor and ignited to generate hot combustion gas.The turbine section extracts energy from the expanding combustion gas,and drives the compressor section via a common shaft. Expandedcombustion products are exhausted downstream, and energy is delivered inthe form of rotational energy in the shaft, reactive thrust from theexhaust, or both.

Gas turbine engines provide efficient, reliable power for a wide rangeof applications in aviation, transportation and industrial powergeneration. Small-scale gas turbine engines typically utilize aone-spool design, with co-rotating compressor and turbine sections.Larger-scale combustion turbines including jet engines and industrialgas turbines (IGTs) are generally arranged into a number of coaxiallynested spools. The spools operate at different pressures, temperaturesand spool speeds, and may rotate in different directions.

Individual compressor and turbine sections in each spool may also besubdivided into a number of stages, formed of alternating rows of rotorblade and stator vane airfoils. The airfoils are shaped to turn,accelerate and compress the working fluid flow, or to generate lift forconversion to rotational energy in the turbine.

Industrial gas turbines often utilize complex nested spoolconfigurations, and deliver power via an output shaft coupled to anelectrical generator or other load, typically using an external gearbox.In combined cycle gas turbines (CCGTs), a steam turbine or othersecondary system is used to extract additional energy from the exhaust,improving thermodynamic efficiency. Gas turbine engines are also used inmarine and land-based applications, including naval vessels, trains andarmored vehicles, and in smaller-scale applications such as auxiliarypower units.

Aviation applications include turbojet, turbofan, turboprop andturboshaft engine designs. In turbojet engines, thrust is generatedprimarily from the exhaust. Modern fixed-wing aircraft generally employturbofan and turboprop configurations, in which the low pressure spoolis coupled to a propulsion fan or propeller. Turboshaft engines areemployed on rotary-wing aircraft, including helicopters, typically usinga reduction gearbox to control blade speed. Unducted (open rotor)turbofans and ducted propeller engines also known, in a variety ofsingle-rotor and contra-rotating designs with both forward and aftmounting configurations.

Aviation turbines generally utilize two and three-spool configurations,with a corresponding number of coaxially rotating turbine and compressorsections. In two-spool designs, the high pressure turbine drives a highpressure compressor, forming the high pressure spool or high spool. Thelow-pressure turbine drives the low spool and fan section, or a shaftfor a rotor or propeller. In three-spool engines, there is also anintermediate pressure spool. Aviation turbines are also used to powerauxiliary devices including electrical generators, hydraulic pumps andelements of the environmental control system, for example using bleedair from the compressor or via an accessory gearbox.

Additional turbine engine applications and turbine engine types includeintercooled, regenerated or recuperated and variable cycle gas turbineengines, and combinations thereof. In particular, these applicationsinclude intercooled turbine engines, for example with a relativelyhigher pressure ratio, regenerated or recuperated gas turbine engines,for example with a relatively lower pressure ratio or for smaller-scaleapplications, and variable cycle gas turbine engines, for example foroperation under a range of flight conditions including subsonic,transonic and supersonic speeds. Combined intercooled andregenerated/recuperated engines are also known, in a variety of spoolconfigurations with traditional and variable cycle modes of operation.

Turbofan engines are commonly divided into high and low bypassconfigurations. High bypass turbofans generate thrust primarily from thefan, which accelerates airflow through a bypass duct oriented around theengine core. This design is common on commercial aircraft andtransports, where noise and fuel efficiency are primary concerns. Thefan rotor may also operate as a first stage compressor, or as apre-compressor stage for the low-pressure compressor or booster module.Variable-area nozzle surfaces can also be deployed to regulate thebypass pressure and improve fan performance, for example during takeoffand landing. Advanced turbofan engines may also utilize a geared fandrive mechanism to provide greater speed control, reducing noise andincreasing engine efficiency, or to increase or decrease specificthrust.

Low bypass turbofans produce proportionally more thrust from the exhaustflow, generating greater specific thrust for use in high-performanceapplications including supersonic jet aircraft. Low bypass turbofanengines may also include variable-area exhaust nozzles and afterburneror augmentor assemblies for flow regulation and short-term thrustenhancement. Specialized high-speed applications include continuouslyafterburning engines and hybrid turbojet/ramjet configurations.

Across these applications, turbine performance depends on the balancebetween higher pressure ratios and core gas path temperatures, whichtend to increase efficiency, and the related effects on service life andreliability due to increased stress and wear. This balance isparticularly relevant to gas turbine engine components in the hotsections of the compressor, combustor, turbine and exhaust sections,where active cooling is required to prevent damage due to high gas pathtemperatures and pressures.

SUMMARY

A gas turbine engine component having a cooling hole includes a firstwall having a cooling hole inlet, a second wall generally opposite thefirst wall and having a cooling hole outlet, a metering sectionextending downstream from the inlet and having a hydraulic diameter(d_(h)), and a diffusing section extending from the metering section tothe outlet. The metering section includes a substantially convex firstsurface extending from a first end to a second end, a substantiallyconcave second surface extending from a third end to a fourth end, afirst curved portion connecting the first end and the third end, and asecond curved portion connecting the second end and the fourth end.

A gas turbine engine component wall includes opposing first and secondwall surfaces, an inlet at the first wall surface, an outlet at thesecond wall surface, a metering section commencing at the inlet andhaving a hydraulic diameter (d_(h)), and a diffusing section incommunication with the metering section and terminating at the outlet.The metering section includes a top portion having a first arcuatesurface that extends from a first end to a second end, a bottom portionhaving a second arcuate surface that extends from a third end to afourth end where the first arcuate surface and the second arcuatesurface have arcs extending in substantially similar directions, a firstcurved portion connecting the first end and the third end and having afirst radius such that a ratio of the first radius to the hydraulicdiameter of the metering section is between 0.1 and 8, and a secondcurved portion connecting the second end and the fourth end and having asecond radius such that a ratio of the second radius to the hydraulicdiameter of the metering section is between 0.1 and 8.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a cross-sectional view of a gas turbine engine.

FIG. 2A is a perspective view of an airfoil for the gas turbine engine,in a rotor blade configuration.

FIG. 2B is a perspective view of an airfoil for the gas turbine engine,in a stator vane configuration.

FIG. 3 is a schematic view of a wall having film cooling holes withcurved metering sections.

FIG. 4 is a sectional view of a cooling hole of FIG. 3 taken along theline 4-4.

FIG. 5 is a view of the cooling hole of FIG. 4 taken along the line 5-5.

FIG. 6 is a perspective view of the cooling hole of FIG. 4 with theouter wall removed.

FIG. 7 is a cross-sectional view of the cooling hole of FIG. 6 takenalong the line 7-7.

FIG. 8 is a cross-sectional view of the outline of the metering sectionof another embodiment of a cooling hole with a curved metering section.

FIG. 9 is a cross-sectional view of the outline of the metering sectionof another embodiment of a cooling hole with a curved metering section.

FIG. 10 is a perspective view of another embodiment of a cooling holewith a curved metering section.

FIG. 11 is a cross-sectional view of the cooling hole of FIG. 10 takenalong the line 11-11.

FIG. 12A is a simplified flow diagram illustrating one embodiment of amethod for producing a cooling hole in a gas turbine engine componentwall.

FIG. 12B is a simplified flow diagram illustrating another embodiment ofa method for producing a cooling hole in a gas turbine engine componentwall.

FIG. 13A is a sectional view of another embodiment of a cooling holetaken along the line 4-4 as shown in FIG. 3.

FIG. 13B is a sectional view of another embodiment of a cooling holetaken along the line 4-4 as shown in FIG. 3.

FIG. 14A is a view of the cooling hole of FIG. 13A looking from theoutlet toward the inlet.

FIG. 14B is a perspective view of the cooling hole of FIG. 13A.

FIG. 15A is a view of one embodiment of the cooling hole of FIG. 14taken along the line 5-5 as shown in FIG. 4.

FIG. 15B is a view of another embodiment of the cooling hole of FIG. 14taken along the line 5-5 as shown in FIG. 4.

FIGS. 15C and 15D are views of other embodiments of the cooling hole ofFIG. 14 taken along the line 5-5 as shown in FIG. 4.

DETAILED DESCRIPTION

FIG. 1 is a cross-sectional view of gas turbine engine 10. Gas turbineengine (or turbine engine) 10 includes a power core with compressorsection 12, combustor 14 and turbine section 16 arranged in flow seriesbetween upstream inlet 18 and downstream exhaust 20. Compressor section12 and turbine section 16 are arranged into a number of alternatingstages of rotor airfoils (or blades) 22 and stator airfoils (or vanes)24.

In the turbofan configuration of FIG. 1, propulsion fan 26 is positionedin bypass duct 28, which is coaxially oriented about the engine corealong centerline (or turbine axis) C_(L). An open-rotor propulsion stage26 may also provided, with turbine engine 10 operating as a turboprop orunducted turbofan engine. Alternatively, fan rotor 26 and bypass duct 28may be absent, with turbine engine 10 configured as a turbojet orturboshaft engine, or an industrial gas turbine.

For improved service life and reliability, components of gas turbineengine 10 are provided with an improved cooling configuration, asdescribed below. Suitable components for the cooling configurationinclude rotor airfoils 22, stator airfoils 24 and other gas turbineengine components exposed to hot gas flow, including, but not limitedto, platforms, shrouds, casings and other endwall surfaces in hotsections of compressor 12 and turbine 16, and liners, nozzles,afterburners, augmentors and other gas wall components in combustor 14and exhaust section 20.

In the two-spool, high bypass configuration of FIG. 1, compressorsection 12 includes low pressure compressor (LPC) 30 and high pressurecompressor (HPC) 32, and turbine section 16 includes high pressureturbine (HPT) 34 and low pressure turbine (LPT) 36. Low pressurecompressor 30 is rotationally coupled to low pressure turbine 36 via lowpressure (LP) shaft 38, forming the LP spool or low spool. High pressurecompressor 32 is rotationally coupled to high pressure turbine 34 viahigh pressure (HP) shaft 40, forming the HP spool or high spool.

Flow F at inlet 18 divides into primary (core) flow F_(P) and secondary(bypass) flow F_(S) downstream of fan rotor 26. Fan rotor 26 acceleratessecondary flow F_(S) through bypass duct 28, with fan exit guide vanes(FEGVs) 42 to reduce swirl and improve thrust performance. In somedesigns, structural guide vanes (SGVs) 42 are used, providing combinedflow turning and load bearing capabilities.

Primary flow F_(P) is compressed in low pressure compressor 30 and highpressure compressor 32, then mixed with fuel in combustor 14 and ignitedto generate hot combustion gas. The combustion gas expands to providerotational energy in high pressure turbine 34 and low pressure turbine36, driving high pressure compressor 32 and low pressure compressor 30,respectively. Expanded combustion gases exit through exhaust section (orexhaust nozzle) 20, which can be shaped or actuated to regulate theexhaust flow and improve thrust performance.

Low pressure shaft 38 and high pressure shaft 40 are mounted coaxiallyabout centerline C_(L), and rotate at different speeds. Fan rotor (orother propulsion stage) 26 is rotationally coupled to low pressure shaft38. In advanced designs, fan drive gear system 44 is provided foradditional fan speed control, improving thrust performance andefficiency with reduced noise output.

Fan rotor 26 may also function as a first-stage compressor for gasturbine engine 10, and LPC 30 may be configured as an intermediatecompressor or booster. Alternatively, propulsion stage 26 has an openrotor design, or is absent, as described above. Gas turbine engine 10thus encompasses a wide range of different shaft, spool and turbineengine configurations, including one, two and three-spool turboprop and(high or low bypass) turbofan engines, turboshaft engines, turbojetengines, and multi-spool industrial gas turbines.

In each of these applications, turbine efficiency and performance dependon the overall pressure ratio, defined by the total pressure at inlet 18as compared to the exit pressure of compressor section 12, for exampleat the outlet of high pressure compressor 32, entering combustor 14.Higher pressure ratios, however, also result in greater gas pathtemperatures, increasing the cooling loads on rotor airfoils 22, statorairfoils 24 and other components of gas turbine engine 10. To reduceoperating temperatures, increase service life and maintain engineefficiency, these components are provided with improved coolingconfigurations, as described below. Suitable components include, but arenot limited to, cooled gas turbine engine components in compressorsections 30 and 32, combustor 14, turbine sections 34 and 36, andexhaust section 20 of gas turbine engine 10.

FIG. 2A is a perspective view of rotor airfoil (or blade) 22 for gasturbine engine 10, as shown in FIG. 1, or for another turbomachine.Rotor airfoil 22 extends axially from leading edge 51 to trailing edge52, defining pressure surface 53 (front) and suction surface 54 (back)therebetween.

Pressure and suction surfaces 53 and 54 form the major opposing surfacesor walls of airfoil 22, extending axially between leading edge 51 andtrailing edge 52, and radially from root section 55, adjacent innerdiameter (ID) platform 56, to tip section 57, opposite ID platform 56.In some designs, tip section 57 is shrouded.

Cooling holes or outlets 60 are provided on one or more surfaces ofairfoil 22, for example along leading edge 51, trailing edge 52,pressure (or concave) surface 53, or suction (or convex) surface 54, ora combination thereof. Cooling holes or passages 60 may also be providedon the endwall surfaces of airfoil 22, for example along ID platform 56,or on a shroud or engine casing adjacent tip section 57.

FIG. 2B is a perspective view of stator airfoil (or vane) 24 for gasturbine engine 10, as shown in FIG. 1, or for another turbomachine.Stator airfoil 24 extends axially from leading edge 61 to trailing edge62, defining pressure surface 63 (front) and suction surface 64 (back)therebetween. Pressure and suction surfaces 63 and 64 extend from inner(or root) section 65, adjacent ID platform 66, to outer (or tip) section67, adjacent outer diameter (OD) platform 68.

Cooling holes or outlets 60 are provided along one or more surfaces ofairfoil 24, for example leading or trailing edge 61 or 62, pressure(concave) or suction (convex) surface 63 or 64, or a combinationthereof. Cooling holes or outlets 60 may also be provided on the endwallsurfaces of airfoil 24, for example along ID platform 66 and OD platform68.

Rotor airfoils 22 (FIG. 2A) and stator airfoils 24 (FIG. 2B) are formedof high strength, heat resistant materials such as high temperaturealloys and superalloys, and are provided with thermal anderosion-resistant coatings. Airfoils 22 and 24 are also provided withinternal cooling passages and cooling holes 60 to reduce thermal fatigueand wear, and to prevent melting when exposed to hot gas flow in thehigher temperature regions of a gas turbine engine or otherturbomachine. Cooling holes 60 deliver cooling fluid (e.g., steam or airfrom a compressor) through the outer walls and platform structures ofairfoils 22 and 24, creating a thin layer (or film) of cooling fluid toprotect the outer (gas path) surfaces from high temperature flow.

While surface cooling extends service life and increases reliability,injecting cooling fluid into the gas path also reduces engineefficiency, and the cost in efficiency increases with the requiredcooling flow. Cooling holes 60 are thus provided with improved meteringand inlet geometry to reduce jets and blow off, and improved diffusionand exit geometry to reduce flow separation and corner effects. Coolingholes 60 reduce flow requirements and improve the spread of coolingfluid across the hot outer surfaces of airfoils 22 and 24, and other gasturbine engine components, so that less flow is needed for cooling andefficiency is maintained or increased.

The cooling holes described herein provide a cooling solution thatoffers improved film cooling and eliminates or reduces the flowseparation problems associated with conventional diffusion-type filmcooling holes. The shape of the cooling hole metering section ismodified to better direct cooling air to the hole's diffusing section.The described cooling holes provide improved film effectiveness andreduce the likelihood of film separation so that they work as intendedat high blowing ratios.

Some cooling holes include two sections: (1) a metering section at ornear the hole inlet and (2) a diffusing section at or near the holeoutlet. The metering section “meters” the flow of cooling air,regulating the velocity and quantity of air that enters through theinlet. Air flowing through the metering section enters the diffusingsection before reaching the hole outlet. The diffusing section causesthe cooling air to expand (diffuse) so that a wider cooling film isformed. A recent trend in state of the art cooling holes has been tomodify the cooling film by changing the geometry or configuration of thediffusing section of cooling holes. While this technique has yieldedsome improvements in film cooling, it also presents additionaldifficulties. For example, some cooling holes with multi-lobed diffusingsections can diffuse the cooling air too much at high blowing ratios,spreading the cooling film too thinly so that “holes” or “gaps” in thecooling film appear. This phenomenon is called flow separation. Fluid inthe hot gas path adjacent to the cooling hole can mix into these holesor gaps in the cooling film, transferring unwanted heat to the filmcooled component and reducing cooling effectiveness. Additionally,although film cooling hole performance typically improves as the blowingratio is increased, the expansion ratio of the diffuser can be toogreat, resulting in flow separation and incomplete filling of thediffuser section of the cooling hole with cooling air. In thesecircumstances, high temperature gases passing along wall surfaces canmix with the cooling air flowing within the diffuser section of thecooling hole (i.e. hot gas entrainment). The turbulent mixing thatoccurs during hot gas entrainment can adversely impact film coolingeffectiveness and performance of the diffusing section of the coolinghole. Instead of modifying the diffusing section of the cooling hole toreduce the incidence of flow separation and potential entrainment of hotgaspath flow (high temperature gases), which adversely impacts overallcooling hole performance, geometric features are introduced that reducethe propensity of flow separation with highly diffused cooling holegeometries, while also mitigating the amount of turbulent mixing thatoccurs between the expelled film cooling flow and the free stream gaswithin the thermal boundary layer. The cooling holes described hereincontain modified metering section geometry to improve the overall filmcooling performance by improving diffusing section fill characteristicswhile also reducing the amount of downstream film attenuation.

FIG. 3 illustrates a view of a wall of a gas turbine engine componenthaving cooling holes. Wall 100 includes inner wall surface 102 and outerwall surface 104. As described in greater detail below, wall 100 isprimarily metallic and outer wall surface 104 can include a thermalbarrier coating. Cooling holes 106 are oriented so that their inlets arepositioned on the first wall surface 102 and their outlets arepositioned on outer wall surface 104. During gas turbine engineoperation, outer wall surface 104 is in proximity to high temperaturegases (e.g., combustion gases, hot air). Cooling air is delivered insidewall 100 where it exits the interior of the component through coolingholes 106 and forms a cooling film on outer wall surface 104. Thediffusing section of cooling hole 106 can have multiple lobes to aid inthe lateral diffusion of the cooling air as shown in FIG. 3. In thisembodiment, cooling holes 106 have three lobes in the diffusing section.

As described in greater detail below, cooling air enters the meteringsection of cooling hole 106 and flows out of the diffusing section ofcooling hole 106. Cooling holes 106 can be arranged in a row on wall 100as shown in FIG. 3 and positioned axially so that the cooling air flowsin substantially the same direction longitudinally as the hightemperature gases flowing past wall 100. In this embodiment, cooling airpassing through cooling holes 106 exits cooling holes traveling insubstantially the same direction as the high temperature gases flowingalong outer wall surface 104 (represented by arrow H). Here, the linearrow of cooling holes 106 is substantially perpendicular to the directionof flow H. In alternate embodiments, the orientation of cooling holes 16can be arranged on outer wall surface 104 so that the flow of coolingair is substantially perpendicular to the high temperature gas flow(i.e. cooling air exits cooling holes 106 radially) or at an anglebetween parallel and perpendicular (compound angle). Cooling holes 106can also be provided in a staggered formation on wall 100. Cooling holes106 can be located on a variety of components that require cooling.Suitable components include, but are not limited to, turbine vanes andblades, blade or vane platforms, shrouds, endwalls, combustors, bladeouter air seals, augmentors, etc. Cooling holes 106 can be located onthe pressure side or suction side of airfoils. Cooling holes 106 canalso be located on the blade tip.

FIGS. 4 through 7 illustrate one embodiment of cooling hole 106 ingreater detail. FIG. 4 illustrates a sectional view of film cooling hole106 of FIG. 3 taken through the center of cooling hole 106 along theline 4-4. Cooling hole 106 includes inlet 110, metering section 112,diffusing section 114 and outlet 116. Inlet 110 is an opening located oninner wall surface 102. Cooling air C enters cooling hole 106 throughinlet 110 and passes through metering section 112 and diffusing section114 before exiting cooling hole 106 at outlet 116 along outer wallsurface 104.

Metering section 112 is adjacent to and downstream from inlet 110 andcontrols (meters) the flow of cooling air through cooling hole 106. Insome embodiments, metering section 112 has a substantially constant flowarea from inlet 110 to diffusing section 114. Metering sections 112 havea length/and hydraulic diameter d_(h). Hydraulic diameters (d_(h)) areused to describe flow in non-circular channels. In some embodiments,metering section 112 has a length/according to the relationship:d_(h)≦l≦3d_(h). That is, the length of metering section 112 is betweenone and three times its hydraulic diameter. The length of meteringsection 112 can exceed 3d_(h), reaching upwards of 30d_(h). In someembodiments, metering section 112 is inclined with respect to wall 100as illustrated in FIG. 4 (i.e. metering section 112 is not perpendicularto wall 100). Metering section 112 has a longitudinal axis representedby numeral 118.

Diffusing section 114 is adjacent to and downstream from meteringsection 112. Cooling air C diffuses within diffusing section 114 beforeexiting cooling hole 106 along outer wall surface 104. Outer wallsurface 104 includes upstream end 120 (upstream of cooling hole 106) anddownstream end 122 (downstream from cooling hole 106). Diffusing section114 opens along outer wall surface 104 between upstream end 120 anddownstream end 122. As shown in FIG. 4, cooling air C diffuses away fromlongitudinal axis 118 in diffusing section 114 as it flows towardsoutlet 116. Diffusing section 114 can have various configurations.Diffusing section 114 can have multiple lobes as shown in FIGS. 4through 8 and described in greater detail in the U.S. patent applicationentitled “MULTI-LOBED COOLING HOLE AND METHOD OF MANUFACTURE”, filed onFeb. 15, 2012 and having the Attorney Docket No.PA0019059U-U73.12-734KL, which is incorporated by reference. In thisembodiment, diffusing section 114 includes lobes 124, 126 and 128 asshown in FIG. 5. In other embodiments, diffusing section 114 is a moreconventional diffusing section such as those described in U.S. Pat. No.4,197,443 or U.S. Pat. No. 4,684,323.

To improve the flow of cooling air C through cooling hole 106, meteringsection 112 does not possess the conventional circular, oblong (oval orelliptical) or racetrack (oval with two parallel sides having straightportions) cross-sectional geometries common in some cooling holes.Instead, metering section 112 includes at least two arcuate surfacesthat have arcs that extend in a substantially similar direction.

FIG. 6 illustrates a perspective view of the cooling hole of FIG. 4. Forthe purposes of illustration, wall 100 has been removed from the figureto better show cooling hole 106. Metering section 112 includes topportion 130 and bottom portion 132. Top portion 130 includes firstarcuate surface 134, and bottom portion 132 includes second arcuatesurface 136. As shown in FIG. 6, first arcuate surface 134 and secondarcuate surface 136 define flowpath 138 of metering section 112. Firstarcuate surface 134 is located on wall 100 between outer wall surface104 and flowpath 138 (shown best in FIG. 7). Second arcuate surface 136is located on wall 100 between inner wall surface 102 and flowpath 138(shown best in FIG. 7). As shown in FIG. 6, first arcuate surface 134and second arcuate surface 136 each form arcs that extend in asubstantially similar direction. First arcuate surface 134 is convex;the surface extending towards the center of flowpath 138. Second arcuatesurface 136 is concave; the surface extending away from the center offlowpath 138. Due to the convex and concave geometries of these twosurfaces, the arc formed by first arcuate surface 134 and the arc formedby second arcuate surface 136 both extend in a generally downwarddirection as shown in FIGS. 6 and 7.

First arcuate surface 134 and second arcuate surface 136 extend as shownin FIG. 6 for the entire length of metering section 112 (i.e. from inlet110 to diffusing section 114). In some embodiments, first arcuatesurface 134 also extends through diffusing section 114 from inlet 110 tooutlet 116 as shown in FIGS. 4 and 6. In some embodiments, meteringsection 112 has a length greater than d_(h), where d_(h) is thehydraulic diameter of metering section 112.

FIG. 7 illustrates a cross-sectional outline of metering section 112 offilm cooling hole 106 of FIG. 6 taken along the line 7-7. For thepurposes of illustration, wall 100 has been removed from the figure tobetter show cooling hole 106. FIG. 7 shows metering section 112 from theperspective of diffusing section 114 (i.e. the viewer is lookingstraight through metering section 112 towards inlet 110).

In some embodiments, first arcuate surface 134 and second arcuatesurface 136 intersect. First arcuate surface 134 includes first end 140and second end 142. Second arcuate surface 136 includes first end 144and second end 146. As illustrated in FIG. 7, first end 140 of firstarcuate surface 134 and first end 144 of second arcuate surface 136intersect and second end 142 of first arcuate surface 134 and second end146 of second arcuate surface 136 intersect. In this embodiment,flowpath 138 is crescent shaped. For first arcuate surface 134 andsecond arcuate surface 136 to intersect, first arcuate surface 134 andsecond arcuate surface 136 must have different curvatures (i.e. thedegree of surface “flatness”).

The curved geometry of metering section 112 produces a “covered” region(near top portion 130) where first arcuate surface 134 of meteringsection 112 prevents cooling air C from diffusing in a forward direction(towards upstream end 120), enabling cooling air C to be “retained” fora longer period of time beneath first arcuate surface 134 beforeexpanding into diffusing section 114. The covered region segregates thehigh temperature gases flowing along wall 100 from cooling air C andreduces the initial expansion ratio of cooling air C at the upstream endof diffusing section 114 of cooling hole 106. The increased residencetime of cooling air C in metering section 112 combined with the reducedexpansion ratio at the inlet of diffusing section 114 improves the fillcharacteristics of the cooling air as it expands along diffusing section114 of cooling hole 106. This, in turn, lowers the propensity of flowseparation of cooling air C along diffusing section 114 due tooverexpansion and flow vorticity.

In other embodiments, first arcuate surface 134 and second arcuatesurface 136 have substantially identical curvature. When first arcuatesurface 134 and second arcuate surface 136 have identical curvature, thetwo surfaces cannot form flowpath 138 where ends 144 and 146 of secondarcuate surface 136 both intersect with first arcuate surface 134. Inthese embodiments, metering section 112 also includes first and secondside surfaces. FIG. 8 illustrates a cross-sectional view of the meteringsection of one such embodiment of a film cooling hole (flowpath 138A).First arcuate surface 134A is concave and second arcuate surface 136A isconvex, each surface having identical curvature. First side surface 148connects first end 140 of first arcuate surface 134A with first end 144of second arcuate surface 136A. Second side surface 150 connects secondend 142 of first arcuate surface 134A with second end 146 of secondarcuate surface 136A. First side surface 148 and second side surface 150can be curved (convex) as shown in FIG. 8. Alternatively, first sidesurface 148 and second side surface 150 can be straight.

In some embodiments, the arcs of first arcuate surface 134 and secondarcuate surface 136 extend in substantially similar, but not identical,directions. FIG. 9 illustrates a cross-sectional view of the meteringsection of a film cooling hole in which the arcs of surfaces 134 and 136extend in different directions (flowpath 138B), but generally in onedirection. First arcuate surface 134B extends in a direction that isgenerally downward and to the left (represented by arrow A). First end140 and second end 142 have different elevations relative to outer wallsurface 104. Second arcuate surface 136B extends in a direction that isgenerally downward and to the right (represented by arrow B). The arcsof both first arcuate surface 134B and second arcuate surface 136Bextend generally downward, but also left and right to different degrees.

FIG. 10 illustrates a perspective view of another embodiment of acooling hole having a curved metering section. For the purposes ofillustration, wall 100 has been removed from the figure to better showcooling hole 106C. Metering section 112C includes top portion 130C andbottom portion 132C. Top portion 130C includes first arcuate surface134C, and bottom portion 132C includes second arcuate surface 136C. Asshown in FIG. 10, first arcuate surface 134C and second arcuate surface136C define flowpath 138C of metering section 112C. First arcuatesurface 134C is concave; the surface extending away from the center offlowpath 138C. Second arcuate surface 136C is convex; the surfaceextending towards the center of flowpath 138C. Due to the concave andconvex geometries of these two surfaces, the arc formed by first arcuatesurface 134C and the arc formed by second arcuate surface 136C bothextend in a generally upward direction as shown in FIGS. 10 and 11.

Also, as shown in FIG. 10, convex bottom portion 132C of meteringsection 112C gradually transitions to concave bottom surfaces withindiffusing section 114. The contour lines shown in FIG. 10 illustrate thetransition from convex to concave surfaces. Depending on the positionand flow characteristics of cooling hole 106C, the transition fromconvex bottom surface to concave bottom surface(s) can occur withindiffusing section 114 closer to metering section 112C or closer to thetrailing edge of diffusing section 114. Convex bottom portion 132C cantransition to a single concave bottom surface, or, as shown in FIG. 10,convex bottom portion 132C can transition to a plurality of concavebottom surfaces.

FIG. 11 illustrates a cross-sectional outline of metering section 112Cof film cooling hole 106C of FIG. 10 taken along the line 11-11. For thepurposes of illustration, wall 100 has been removed from the figure tobetter show cooling hole 106C. FIG. 11 shows metering section 112C fromthe perspective of diffusing section 114 (i.e. the viewer is lookingstraight through metering section 112C towards inlet 110).

In addition to the reduced flow separation and fill improvements notedabove, the incorporation of a curved metering shape as depicted in FIGS.10 and 11 modifies the flow structure within the curved metering sectionof the cooling hole geometry by generating counter rotating pairedvortex structures having the opposite direction of vortex structuresobserved in single and multi-lobe diffusing sections of cooling holegeometries with conventional cylindrical metering shapes. The counterrotating vortices generated in curved shape metering section 112Cfunctionally result in anti-vortices, canceling out the vorticesinherently observed in diffusing section 114 of cooling hole 106C. Thecombination of the two flow structures within metering section 112C anddiffusing section 114 of cooling hole 106C (e.g., anti-vortex andvortex) results in an ejection of cooling air C that contains minimal orno vorticity and is laminar in nature (i.e. little disruption). Theejection of laminar-like cooling air C inherently reduces or mitigatesthe amount of turbulent mixing between the high temperature gasesflowing along wall 100 and the film coolant flow. The reduced mixingbetween hot and cold fluids reduces the attenuation rate of the filmcooling boundary layer, resulting in significantly increased adiabaticfilm effectiveness and film cooling performance.

By configuring flowpaths 138, 138A, 138B and 138C as described usingsurfaces that have arcs that extend in a substantially similardirection, cooling air C is better prepared to spread laterally withindiffusing section 114 with minimal flow separation. Flowpaths 138, 138Band 138C reduce the likelihood that cooling air C will diffuse in anupward (with respect to FIG. 7) direction (i.e. forward diffusion). Whenforward diffusion occurs, some cooling air C does not enter diffusingsection 114 and jets or blows off away from outer wall surface 104,resulting in reduced or incomplete formation of the film of cooling airmeant to cool outer wall surface 104. Flowpaths 138, 138B and 138Cencourage cooling air C to diverge laterally (left and right withrespect to FIGS. 7, 9 and 10) within metering section 112 and once itreaches lobes 124, 126 and 128 of diffusing section 114. Flowpath 138Aencourages cooling air C to flow into the lower left and right cornersof metering section 112 (FIG. 8) and also to attach to second arcuatesurface 136A to prevent “jet off” or “blow off” at high blowing ratios.

The embodiments of cooling hole 106 described herein allow the use ofhigh blowing ratios of cooling air C. As the blowing ratio increases,the pressure gradient across cooling hole 106 increases. When thepressure gradient across cooling hole 106 is increased, cooling air C isforced to fill the extremities (corners, edges, etc.) of flowpath 138.By filling the entire flowpath 138 with cooling air C, the air flow isless likely to separate one it reaches diffusing section 114 and beginsto expand. Thus, flowpaths 138, 138A, 138B and 138C improve the fillingof diffusing section 114 with cooling air C. By extending the length (L)of first arcuate surface 134, forward diffusion of cooling air C isfurther prevented, reducing the expansion ratio of cooling air indiffusing section 114 immediately downstream of metering section 112.

By reducing or eliminating forward diffusion and encouraging lateraldiffusion at high blowing ratios, diffusing section 114 is able toprovide a better film of cooling air along outer wall surface 104 andcool the gas turbine engine component. Producing a better film ofcooling air provides cooling solution flexibility. The number of coolingholes 106 needed to cool the component can be reduced, the temperatureof cooling air C used to cool the component can be increased or thecomponent can be exposed to higher temperature environments withoutoverheating. The cooling holes described herein will provide improvedfilm cooling at any blowing ratio, but are particularly suited forblowing ratios between about 0.5 and 10 where the blowing ratio (massflux ratio) is calculated according to the equation:

M=ρ _(f) V _(f) ¹/ρ_(∞) V _(∞)

First arcuate surface 134, second arcuate surface 136, first sidesurface 148 and second side surface 150 can also includevortex-generating structures such as those described in U.S. patentapplication Ser. No. 12/157,115. Vortex-generating structures present onsurfaces 134, 136, 148 and/or 150 can be used to negate flow vorticesthat are created elsewhere in cooling hole 106 to prevent the formationof kidney vortices at outlet 116 and the unwanted entrainment of hightemperature gas into the cooling air film.

The gas turbine engine components, gas path walls and cooling passagesdescribed herein can thus be manufactured using one or more of a varietyof different processes. These techniques provide each cooling hole andcooling passage with its own particular configuration and features,including, but not limited to, inlet, metering, transition, diffusion,outlet, upstream wall, downstream wall, lateral wall, longitudinal, lobeand downstream edge features, as described above. In some cases,multiple techniques can be combined to improve overall coolingperformance or reproducibility, or to reduce manufacturing costs.

Suitable manufacturing techniques for forming the cooling configurationsdescribed here include, but are not limited to, electrical dischargemachining (EDM), laser drilling, laser machining, electrical chemicalmachining (ECM), water jet machining, casting, conventional machiningand combinations thereof. Electrical discharge machining includes bothmachining using a shaped electrode as well as multiple pass methodsusing a hollow spindle or similar electrode component. Laser machiningmethods include, but are not limited to, material removal by ablation,trepanning and percussion laser machining. Conventional machiningmethods include, but are not limited to, milling, drilling and grinding.

The gas flow path walls and outer surfaces of some gas turbine enginecomponents include one or more coatings, such as bond coats, thermalbarrier coatings, abrasive coatings, abradable coatings and erosion orerosion-resistant coatings. For components having a coating, the inlet,metering portion, transition, diffusion portion and outlet coolingfeatures may be formed prior to coating application, after a firstcoating (e.g., a bond coat) is applied, or after a second or third(e.g., interlayer) coating process, or a final coating (e.g.,environmental or thermal barrier) coating process. Depending oncomponent type, cooling hole or passage location, repair requirementsand other considerations, the diffusion portion and outlet features maybe located within a wall or substrate, within a thermal barrier coatingor other coating layer applied to a wall or substrate, or based oncombinations thereof. The cooling geometry and other features may remainas described above, regardless of position relative to the wall andcoating materials or airfoil materials.

In addition, the order in which cooling features are formed and coatingsare applied may affect selection of manufacturing techniques, includingtechniques used in forming the inlet, metering portion, transition,outlet, diffusion portion and other cooling features. For example, whena thermal barrier coat or other coating is applied to the outer surfaceof a gas path wall before the cooling hole or passage is produced, laserablation or laser drilling may be used. Alternatively, either laserdrilling or water jet machining may be used on a surface without athermal barrier coat. Additionally, different machining methods may bemore or less suitable for forming different features of the cooling holeor cooling passage, for example, different EDM, laser machining andother machining techniques may be used for forming the outlet anddiffusion features, and for forming the transition, metering and inletfeatures.

FIG. 12A is a simplified flow diagram illustrating one embodiment of amethod for producing a cooling hole with a curved metering section in agas turbine engine wall having inner and outer surfaces. Method 200includes forming a metering section between the inner and outer surfaces(step 202) and forming a diffusing section between the metering sectionand the outer surface (step 204). The metering section formed includes atop surface (first arcuate surface 134) and a bottom surface (secondarcuate surface 136). Each surface (surfaces 134 and 136) has an arcthat extends in a substantially similar direction. Metering section 112is formed in step 202 by one or more of the casting, machining ordrilling techniques described above. The technique(s) chosen is/aretypically determined based on performance, reproducibility and cost. Inembodiments where step 202 occurs prior to step 204, inlet 110 andportions of diffusing section 114 and outlet 116 can also be formedduring formation of metering section 112. Diffusing section 114 isformed in step 204 by one or more of the casting, machining or drillingtechniques described above. As with metering section 112, thetechnique(s) chosen is/are typically determined based on performance,reproducibility and cost. In embodiments where step 202 occurs prior tostep 204, outlet 116 is fully formed during step 204. Steps 202 and 204can be performed before or after an optional thermal barrier coatingapplication. In optional step 206 (shown as a step in method 200A inFIG. 12B), a thermal barrier coating is applied to outer wall surface104. Application of the thermal barrier coating can also include theapplication of a bond coating prior to the thermal barrier coating.Steps 202, 204 and step 206 can be performed in any order depending onthe location of cooling hole 106 and the location of diffusing section114 relative to the metallic wall and the thermal barrier coating. Aspreviously stated, the order of steps 202, 204 and step 206 can affectthe machining or drilling techniques chosen for steps 202 and 204.

FIGS. 13A, 13B, 14A, 14B, 15A, 15B, 15C and 15D illustrate additionalembodiments of cooling holes having curved metering sections. FIGS. 13Aand 13B are similar to the view shown in FIG. 4 and are meant toillustrate different embodiments of the bottom surface of diffusingsection 114 compatible with the described curved metering sections. Asshown in FIG. 13A, the bottom surface of diffusing section 114 canextend from metering section 112 to outlet 116 in a linear fashion(i.e., a straight diffuser). Alternatively, as shown in FIG. 13B, thebottom surface of diffusing section 114 can extend from metering section112 to outlet 116 in a convex fashion (i.e., a convex diffuser). Inother embodiments, the bottom surface of diffusing section 114 caninclude a portion that is linear and a portion that is convex.

FIG. 14A illustrates a view looking through one embodiment of coolinghole 106 from outlet 116 to inlet 110. FIG. 14A is similar to the viewshown in FIG. 7. FIG. 14B illustrates a perspective view of cooling hole106 shown in FIG. 14A. Metering section 112D is defined by first arcuatesurface 134D, second arcuate surface 136D, first curved portion 152 andsecond curved portion 154. First arcuate surface 134D extends from firstend 140D to second end 142D. Second arcuate surface 136D extends fromfirst end 144D to second end 146D.

Instead of the ends of first arcuate surface 134D and second arcuatesurface 136D meeting (as shown in FIG. 7), the ends of first arcuatesurface 134D and second arcuate surface 136D are connected by separatecurved portions. First curved portion 152 connects first end 140D offirst arcuate surface 134D and first end 144D of second arcuate surface136D. Second curved portion 154 connects second end 142D of firstarcuate surface 134D and second end 146D of second arcuate surface 136D.

In some embodiments, first curved portion 152 and second curved portion154 are arcuate portions, each having a radius of curvature. Firstcurved portion 152 and second curved portion 154 can have the sameradius of curvature or different degrees of curvature. In someembodiments, a ratio of the radius of curvature of first curved portion152 (and/or second curved portion 154) to the hydraulic diameter ofmetering section 112 (d_(h)) is between 0.1 and 8. In more particularembodiments, the ratio of the radius of curvature of first curvedportion 152 (and/or second curved portion 154) to the hydraulic diameterof metering section 112 is between 0.5 and 4. These ratios of curvaturefor first curved portion 152 and second curved portion 154 to thehydraulic diameter of metering section 112D create beneficial coolingvortices in metering section 112D that counteract the kidney vorticesobserved in state of the art film cooling holes. Together, surfaces134D, 136D, 142D and 144D create a beneficial vortex that moves themajority of cooling flow near the perimeters of metering section 112D(i.e. surfaces 134D, 136D, 142D and 144D). This spreads out the coolingair flow within metering section 112D, which then spills out intodiffusing section 114, enabling the majority of the cooling air flow toreach the opposite sides of diffusing section 114 (shown in FIG. 14A byarrows A and B). This cooling air flow provides momentum to the coolingair flow so that cooling hole 106 forms a cooling film in the regions ofarrows A and B that counteract the kidney vortices that carry the hotgas path air (arrow H in FIG. 4) and try to bring the hot gas path airto the surface of outer wall surface 104. The beneficial cooling vortexcreated by metering section 112D provides improved cooling performanceand film effectiveness and reduces operational metal temperatures ofcomponents in which these cooling holes are deployed.

FIGS. 15A, 15B, 15C and 15D illustrate some embodiments of diffusingsections 114 that can benefit from metering section 112 describedherein. FIG. 15A illustrates a straight diffuser, FIG. 15B illustrates athree-lobed diffuser with a non-linear downstream trailing edge, FIG.15C illustrates a two-lobed diffuser and FIG. 15D illustrates athree-lobed diffuser with a straight downstream trailing edge. FIG. 14Dillustrates a two-lobed diffuser with a straight downstream trailingedge. In each of these diffusing sections 114, the configuration ofmetering section 112D described above improves the cooling performanceof cooling holes 106 when compared to cooling holes with a meteringsection having a circular, oval or elliptical cross section.

While the invention has been described with reference to exemplaryembodiments, it will be understood by those skilled in the art thatvarious changes may be made and equivalents may be substituted forelements thereof without departing from the scope of the invention. Inaddition, many modifications may be made to adapt a particular situationor material to the teachings of the invention without departing from theessential scope thereof. Therefore, it is intended that the inventionnot be limited to the particular embodiments disclosed, but that theinvention will include all embodiments falling within the scope of theappended claims.

1. A gas turbine engine component having a cooling hole, the componentcomprising: a first wall comprising a cooling hole inlet; a second wallgenerally opposite the first wall and comprising a cooling hole outlet;a metering section extending downstream from the inlet and having ahydraulic diameter (d_(h)), the metering section comprising: asubstantially convex first surface extending from a first end to asecond end; a substantially concave second surface extending from athird end to a fourth end; a first curved portion connecting the firstend and the third end; and a second curved portion connecting the secondend and the fourth end; and a diffusing section extending from themetering section to the outlet.
 2. The component of claim 1, wherein thefirst curved portion has a first radius such that a ratio of the firstradius to the hydraulic diameter of the metering section is between 0.1and 8, and wherein the second curved portion has a second radius suchthat a ratio of the second radius to the hydraulic diameter of themetering section is between 0.1 and
 8. 3. The component of claim 2,wherein the ratio of the first radius to the hydraulic diameter of themetering section is between 0.5 and 4, and wherein the ratio of thesecond radius to the hydraulic diameter of the metering section isbetween 0.5 and
 4. 4. The component of claim 1, wherein the meteringsection has a length that is greater than the hydraulic diameter of themetering section.
 5. The component of claim 1, wherein the diffusingsection comprises first and second lobes that each divergelongitudinally and laterally from a central axis of the cooling hole. 6.The component of claim 5, wherein the diffusing section comprises athird lobe positioned between the first and second lobes.
 7. Thecomponent of claim 5, wherein the cooling hole outlet includes astraight downstream trailing edge that extends between the first andsecond lobes.
 8. The component of claim 1, wherein the convex firstsurface and the concave second surface have differing curvature.
 9. Thecomponent of claim 1, wherein the substantially convex first surface ofthe metering section is a bottom surface, and wherein the substantiallyconvex first surface transitions to a concave bottom surface within thediffusing section.
 10. The component of claim 1, wherein the filmcooling hole is located on a component selected from the groupconsisting of blade airfoils, vane airfoils, blade platforms, vaneplatforms, combustor liners, blade outer air seals, blade shrouds,augmentors and endwalls.
 11. The component of claim 1, wherein theconvex first surface comprises an arc that is curved to extend towardsthe concave second surface, and wherein the concave second surfacecomprises an arc that is curved to extend away from the convex firstsurface.
 12. The component of claim 1, wherein the first radius and thesecond radius are equal.
 13. The component of claim 1, wherein a bottomsurface of the diffusing section extends linearly from the meteringsection to the outlet.
 14. The component of claim 1, wherein a bottomsurface of the diffusing section extends in a convex fashion from themetering section to the outlet.
 15. The component of claim 1, wherein aportion of a bottom surface of the diffusing section between themetering section and the outlet is convex.
 16. A gas turbine enginecomponent wall comprising: opposing first and second wall surfaces; aninlet at the first wall surface; an outlet at the second wall surface; ametering section commencing at the inlet and having a hydraulic diameter(d_(h)), the metering section comprising: a top portion having a firstarcuate surface that extends from a first end to a second end; a bottomportion having a second arcuate surface that extends from a third end toa fourth end, wherein the first arcuate surface and the second arcuatesurface have arcs extending in substantially similar directions; a firstcurved portion connecting the first end and the third end and having afirst radius such that a ratio of the first radius to the hydraulicdiameter of the metering section is between 0.1 and 8; and a secondcurved portion connecting the second end and the fourth end and having asecond radius such that a ratio of the second radius to the hydraulicdiameter of the metering section is between 0.1 and 8; and a diffusingsection in communication with the metering section and terminating atthe outlet.
 17. The wall of claim 16, wherein the first arcuate surfaceis curved so that its arc extends away from the bottom portion and thesecond arcuate surface is curved so that its arc extends towards the topportion.
 18. The wall of claim 16, wherein the first arcuate surface isconvex curved so that its arc extends towards the bottom portion and thesecond arcuate surface is concave curved so that its arc extends awayfrom the top portion.
 19. The wall of claim 16, wherein the meteringsection has a hydraulic diameter, and wherein the metering section has alength that is greater than the hydraulic diameter of the meteringsection.